EP2239478B1 - Joint homocinétique du type fixe - Google Patents

Joint homocinétique du type fixe Download PDF

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Publication number
EP2239478B1
EP2239478B1 EP10007894A EP10007894A EP2239478B1 EP 2239478 B1 EP2239478 B1 EP 2239478B1 EP 10007894 A EP10007894 A EP 10007894A EP 10007894 A EP10007894 A EP 10007894A EP 2239478 B1 EP2239478 B1 EP 2239478B1
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EP
European Patent Office
Prior art keywords
cage
inner ring
track
spherical surface
constant velocity
Prior art date
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Active
Application number
EP10007894A
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German (de)
English (en)
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EP2239478A1 (fr
Inventor
Kenta c/o NTN Corporation Yamazaki
Minoru c/o NTN Corporation Ishijima
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NTN Corp
Original Assignee
NTN Corp
NTN Toyo Bearing Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from JP2003343173A external-priority patent/JP4554181B2/ja
Priority claimed from JP2004031130A external-priority patent/JP4712304B2/ja
Application filed by NTN Corp, NTN Toyo Bearing Co Ltd filed Critical NTN Corp
Publication of EP2239478A1 publication Critical patent/EP2239478A1/fr
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Publication of EP2239478B1 publication Critical patent/EP2239478B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
    • F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
    • F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
    • F16D3/224—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts the groove centre-lines in each coupling part lying on a sphere
    • F16D3/2245—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts the groove centre-lines in each coupling part lying on a sphere where the groove centres are offset from the joint centre
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
    • F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
    • F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
    • F16D2003/22303—Details of ball cages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
    • F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
    • F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
    • F16D2003/22313—Details of the inner part of the core or means for attachment of the core on the shaft
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S464/00—Rotary shafts, gudgeons, housings, and flexible couplings for rotary shafts
    • Y10S464/904—Homokinetic coupling
    • Y10S464/906—Torque transmitted via radially spaced balls

Definitions

  • the present invention relates to a fixed type constant velocity joint which can be utilized in various steering devices including electric power steering devices and also in drive shafts, propeller shafts and other power transmission systems in automobiles and various industrial machines.
  • Cardan joints cross shaft couplings
  • the Cardan joint is a non-constant velocity joint which is such that when the working angle increases, the rotational variation between the input and output shafts also increases. Since it is necessary to secure constant velocity nature by combining a plurality of Cardan joints, there is a problem that the degree of freedom of design of vehicles is impaired.
  • the fixed type constant velocity joint comprises an outer ring having a plurality of curved track grooves in its spherical inner surface, an inner ring having a plurality of curved track grooves in its spherical outer surface, torque transmitting balls incorporated between the track grooves of the inner and outer rings, and a cage for holding the torque transmitting balls.
  • the center of curvature of the track grooves of the outer ring (the outer ring track center) is offset with respect to the center of curvature of the spherical inner surface of the outer ring
  • the center of curvature of the track grooves of the inner ring (the inner ring track center) is offset with respect to the center of curvature of the spherical outer surface of the inner ring, axially by the same distance to opposite sides, whereby the ball tracks constituted by the track grooves of the outer and inner rings are in the form of wedges spread toward the opening side of the outer ring.
  • this kind of fixed type constant velocity joint has clearances created therein between the track grooves of the outer and inner rings and the balls because of the request made for functional and processing reasons.
  • the track clearances greatly influence the circumferential play (rotation backlash) between the inner and outer rings.
  • the track clearances are inevitable to the fixed type constant velocity joint from the standpoint of processing allowance and assemblability, resulting in large rotation backlash, causing the fear that such rotation backlash deteriorates the steering feel for substantially straight travel of the vehicle or is the cause of generation of abnormal sounds.
  • Japanese unexamined Patent publication 2003-130082 proposes a fixed type constant velocity joint capable of eliminating or suppressing the rotation backlash by closing the track clearances by a preloading means installed in the joint.
  • the fixed type constant velocity joint disclosed in Japanese unexamined Paten publication 2003-130082 has ball tracks in the form of wedges spread toward the opening side of the outer ring, and in order to close the axial clearances created by track clearances, it has an arrangement wherein a pressing section for axially applying elastic pressing force is provided on the inner ring side, while a receiving section for receiving the pressing force from the pressing section is provided in the cage. And, elastic abutment between the pressing section and the receiving section presses the inner ring toward the opening side of the outer ring, thus producing axial relative movement between the two. The relative movement closes the track clearances through the balls, thus preventing rotation backlash.
  • a fixed type constant velocity joint comprises an outer ring having an inner spherical surface formed with a plurality of track grooves, an inner ring having an outer spherical surface formed with a plurality of track grooves, wedge-shaped ball tracks each defined by an outer ring track groove and an inner ring track groove, which form a pair, and reduced in size from one end of the direction of the axis of the joint to the other end, torque transmitting balls incorporated one in each ball track, and a cage having pockets for holding the torque transmitting balls and interposed between the inner spherical surface of the outer ring and the outer spherical surface of the inner ring, wherein the center of curvature of the track grooves of the outer ring and the center of curvature of the track grooves of the inner ring are offset from the center of the joint by the same distance to opposite sides, said fixed type constant velocity joint being characterized in that the axial position of the pockets of the cage is shifted from the center of curvature of the cage to
  • the amount of shift of the axial central position of the pockets is in such dimensional relation that enables the securement of the clearance between the inner ring and the cage necessary for closing the track clearances by preloading.
  • the amount of shift of the axial central position of the pockets be from 1.0% to 3.0% of the amount of offset of the track grooves. Said dimensional relation can secure a large clearance between the inner ring 2 and the cage on the outer ring innermost part side, reliably avoiding interference between the inner ring and the cage during the cross operation, thus providing smooth and stabilized operability. If said amount of shift is too small, the inner ring and the cage interfere with each other on the outer ring innermost part side during the cross operation.
  • the difference between the axial dimension of the pockets of the cage and the diameter of the torque transmitting balls be in the range from 0 to 30 ⁇ m. While positive clearance setting is preferable for lowering the resistance value, too large clearance makes it impossible to suppress the behavior of the torque transmitting balls, resulting in a failure in smooth operation. Said range ensures stabilized rotation of the torque transmitting balls.
  • Rzeppa type which is a kind of fixed type constant velocity joint
  • UJ undercut free type
  • the fixed type constant velocity joint as shown in Fig. 1 , has as its main structural elements an outer ring 1, an inner ring 2, a plurality of torque transmitting balls 3, and a cage 4.
  • the outer ring 1 has an inner spherical surface 1b, which is formed with axially extending track grooves 1a.
  • the inner ring 2 has an outer spherical surface 2b, which is formed with axially extending track grooves 2a.
  • the cage 4 is interposed between the inner spherical surface 1b of the outer ring 1 and the outer spherical surface 2b of the inner ring 2 and has circumferentially equispaced pockets 4a for receiving the torque transmitting balls 3.
  • the track grooves 1a and 2a are each 6 in number, for example, but in some cases they may be 3 or 8 each; they are not particularly limited in number. When seen in a longitudinal section ( Fig. 1 ), the track grooves 1a and 2a are arcuate.
  • a ball track constituted by a pair of track grooves 1 a and 2a is in the form of a wedge reduced in size from the opening side of the outer ring 1 toward the innermost part side.
  • the center of curvature of the inner spherical surface 1b of the outer ring 1 and the center of curvature of the outer spherical surface 4b of the cage 4 both coincide with the joint center O. Further, the center of curvature of the outer spherical surface 2b of the inner ring 2 and the center of curvature of the inner spherical surface 4c of the cage 4 also coincide with the joint center O. Therefore, the amount of offset of the outer ring track center 01 is a distance from the joint center 0 to the outer ring track center O1, while the amount of offset of the inner ring track center 02 is a distance from the joint center 0 to the inner ring track center 02; thus, the two distances are the same.
  • the centers of curvature of the outer spherical surface 4b and inner spherical surface 4c of the cage 4 are shown coinciding with the joint center O, these centers of curvature may be offset by the same distance to opposite sides with the joint center O therebetween as in the case of the track centers O1 and O2.
  • the pressing member 10 Installed at the shaft end of the shaft 5 is a pressing member 10.
  • the pressing member in the illustrated example is composed of a ball as a pressing section 11, a compression spring as an elastic member 12, and a case 13 for assembling the pressing section 11 and elastic member 12.
  • the elastic member 12 acts as an elastic force through the pressing section 11. If the pressing section 11 is spherical at its contact with a receiving section 15, the shape of its remaining portion may be optional.
  • the case 13 is fixed, by a suitable means such as press fitting or a binder, to the front end of the shaft 5 integrated with the inner joint member 2 by serration coupling.
  • a receiving member 14 is attached to the end of the outer ring innermost part side of the cage 4.
  • This receiving member 14 which is in the form of a cover for covering the end opening on the outer ring innermost part side of the cage 4, is composed of a spherical surface 14a shaped as a partial spherical surface, and an attaching section 14b annularly formed around the outer periphery of the spherical surface 14a.
  • the inner surface of the spherical surface 14a (the surface opposed to the shaft 5) is in the form of a concave surface, and this concave surface functions as the receiving section 15 receiving the pressing forced from the pressing section 11.
  • the attaching section 14b is fixed to the end of the cage 4 by a suitable means such as press fitting or welding.
  • the pressing section 11 is disposed on the inner ring side and the receiving section 15 is disposed on the cage side.
  • the pressing section is disposed on the cage side and the receiving section is disposed on the inner ring side.
  • the axial clearance between the inner ring 2 and the cage 4 should be set at 2.5 - 6.5 times as large as the radial clearance due to the track clearances.
  • This magnification that is, the range from 2.5 to 6.5 times is found from the axial distances from the joint center 0 to the outer ring track center 01 and the inner ring track center 02 (track offset quantity) and from the track OCD.
  • the track PCD means the track groove center diameter of the outer ring 1 and the inner ring 2.
  • the magnification of the axial clearance between the inner ring 2 and the cage 4 with respect to the radial clearance due to said track clearances is less than 2.5 times, it becomes difficult to secure the depth necessary for transmitting torque concerning the track grooves 1a and 2a of the outer ring 1 and the inner ring 2.
  • the outer spherical surface 2b of the inner ring 2 is formed with a chamfered section serving as a relief which avoids interference with the inner spherical surface 4c of the cage 4.
  • the inner spherical surface 4c of the cage 4 is shaped as an aspherical surface which suppresses interference with the outer spherical surface of the inner ring 2. This ensures smooth movement of the inner ring 2 relative to the cage 4, securing the amount of movement of the inner ring 2 due to preloading, thus making it possible to close the track clearances more reliably.
  • Fig. 2 shows a case where the end edge, which is on the outer ring opening side, of the outer spherical surface 2b of the inner ring 2 is formed with a tapered chamfered section m (the broken line portion in the illustration showing a conventional shape), and Figs.
  • 3-7 show cases where the end edge, which is on the outer ring opening side, of the outer spherical surface 2b of the inner ring 2 is formed with a chamfered section, as at m2 - m6 (the broken line portion in the illustration showing a conventional shape), consisting of a curved surface having a center of curvature, as at 03 - 07, which is offset axially or radially from the joint center O.
  • the tapered chamfered section m1 of Fig. 2 has a predetermined inclination angle from the end surface of the inner ring 2.
  • Figs. 2 through 7 show the chamfered sections m1 - m6 formed on the end edge, which is on the outer ring opening side, of the outer spherical surface 2b of the inner ring 2, it is also possible, as shown in Figs. 8 - 13 , to form chamfered sections m1' - m6' on the end edge, which is on the outer ring innermost part side, of the outer spherical surface 2b of the inner ring 2.
  • Fig. 8 shows a case where the end edge, which is on the outer ring innermost part side, of the outer spherical surface 2b of the inner ring 2 is formed with a tapered chamfered section m1'.
  • Figs. 8 shows a case where the end edge, which is on the outer ring innermost part side, of the outer spherical surface 2b of the inner ring 2 is formed with a tapered chamfered section m1'.
  • Fig. 14 shows a case where the joint center O portion of the inner spherical surface 4c' of the cage 4 is formed with a flat section p, whose opposite sides are in the form of concave surfaces of radius R' having centers of curvature 08 and 09 which are offset axially or radially from the joint center O
  • Fig. 15 shows a case where the inner spherical surface 4c" of the cage 4 is in the form of a concave surface of radius R'' having a center of curvature 010 which is offset radially from the joint center O.
  • the track clearances are reliably closed and during the cross operation, for structural reasons, the torque transmitting balls 3 cannot stably control the cage 4 to the position of /2 deg, with the result that interference between the outer spherical surface 2b of the inner ring 2 and the inner spherical surface 4c of the cage 4 can be reliably avoided even if the inner ring 2 is pushed in to the innermost part side (the inner ring track center 02 side) of the outer ring 1.
  • the radial clearance of the truck be from 0 to 1.5% of the track PCD and that the radial clearance between the outer ring 1 and the cage 4 be from 0 to 1.7% of the track PCD. If the percentages of these clearances increase, the radial clearance of the track increases, requiring that the axial clearance between the inner ring 2 and the cage 4 be also increased for play-elimination closing purposes. In the case where the joint rotates with high torque, the inner ring 2 moves toward the innermost part of the outer ring 1 because of the shape of the ball tracks.
  • the outer spherical surface 2b of the inner ring 2 and the partial spherical surface 14a of the receiving member 14 interfere with each other before the outer spherical surface 2b of the inner ring 2 and the inner spherical surface 4c of the cage abut against each other.
  • the ratio of the track PCD to the torque transmitting ball be from 1.5 to 4.0. If this ratio is less than 1.5, the strength of the inner ring 2 lowers, and reversely, if it is greater than 4.0, there is the disadvantage that not only does the strength of the cage 4 lower but also the outer diameter of the outer ring 1 increases.
  • the fixed type constant velocity joint for steering purposes disclosed in Japanese unexamined Patent publication 2003-130082 has a preloading means installed therein, thereby eliminating track clearances which form a main factor in producing a play in the direction of rotation, thus mitigating degradation of steerability and abnormal sound production.
  • Fig. 1 in the case where torque is not applied in the direction of rotation of the shaft, for structural reasons, the inner ring 2 and cage 4 are pushed out to the opening side of the outer ring 1 (the outer ring track center 01 side).
  • the cage 4 is axially displaced to the position where the inner spherical surface 1 b of the outer ring 1 and the outer spherical surface 4b of the cage 4 abut against each other, while the inner ring 2 is axially displaced to the position where track clearances disappear. At this time, if the axial clearance between the inner ring 2 and the cage 4 is not greater than the amount by which the inner ring 2 is axially displaced due to the track clearances, play-elimination closing cannot be effected.
  • the inner ring 2 is axially displaced to the position where the cage inner spherical surface 4c on the outer ring innermost part side and the inner ring outer spherical surface 2b abut against each other, with the outer ring inner spherical surface 1 b on the opening side (the outer ring track center O1 side) of the outer ring 1 and the cage outer spherical surface 4b being held abutting against each other as in the usual BJ.
  • the cross operation in the no-load state (in which the shaft 5 is bent in the direction of the working angle with the outer ring 1 fixed in position), unlike the rotational operation, is such that for structural reasons, the torque transmitting balls 3 cannot stably control the cage 4 to the position of /2 deg even if the shaft 5 is bent by deg, with the result that the inner ring 2 is pushed in to the innermost part side (the inner ring track center 02 side) of the outer ring 1.
  • the outer spherical surface 2b of the inner ring 2 and the inner spherical surface 4c of the cage 4 interfere with each other, the interference appearing as a hitch during the cross operation.
  • the operations of tilt-up and tilt-down in tilt steering cannot be smoothly performed, resulting in inoperability under certain circumstances.
  • the position of the pocket 4a of the cage 4 has been basically such that in order to ensure coincidence between the central positions of the inner and outer spherical surfaces 4b and 4c of the cage 4 and the central position of the torque transmitting ball 3, excluding the case where a contact section between the pocket 4a and the torque transmitting ball 3 is not secured during the high angle, the position of the centers of the inner and outer spherical surfaces 4b and 4c of the cage 4 and the pocket 4a of the cage 4 is half the diameter d of the torque transmitting ball 3 (d/2). For this reason, the radial clearance between the inner ring 2 and the cage 4 is (spherical surface clearance) / 2.
  • Figs. 21 and 22 show an example of a steering device.
  • This steering device transmits the rotation of steering wheel 21 to a steering gear 23 through a steering column consisting of one or a plurality of steering shafts 22, thereby converting it into the reciprocation of a tie rod 24.
  • the steering shaft 22 cannot be disposed in a straight line by reason of balance with on-vehicle space and the like, one or a plurality of universal joints 25 are interposed between the steering shafts 22, thereby ensuring that correct rotation can be transmitted to the steering gear 23 even in the state in which the steering shafts 22 are bent.
  • a fixed type constant velocity joint may be used as this universal joint 25.
  • the character in Fig. 22 denotes the bending angle of the joint. Large angles with the bending angle exceeding 30 deg. may be set.
  • the steering device may be an electric power steering device (EPS) adapted to impart auxiliary force by a motor or a hydraulic type power steering device.
  • EPS electric power steering device

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Steering Controls (AREA)
  • Rolling Contact Bearings (AREA)
  • Bearings For Parts Moving Linearly (AREA)
  • Cosmetics (AREA)
  • Agricultural Chemicals And Associated Chemicals (AREA)
  • Pens And Brushes (AREA)

Claims (7)

  1. Joint homocinétique du type fixe, comprenant: une bague externe (1) comportant une surface sphérique interne (1b), formée d'une pluralité de rainures de guidage (1a), une bague intérieure (2) comportant une surface externe sphérique (2b) formée d'une pluralité de rainures de guidage (2a), des rainures à billes en forme de coin, chacune définie par une rainure de guidage de la bague externe (1a) et une rainure de guidage de la bague interne (2a), qui forment une paire, et de taille réduite d'une extrémité de la direction de l'axe du joint à l'autre extrémité, des billes de transmission de moment de rotation (3) incorporées une dans chaque rainure à billes, et une cage (4) comportant des poches (4a) pour maintenir les billes de transmission de moment de rotation et interposées entre la surface sphérique interne (1b) de la bague externe et la surface sphérique externe (2b) de la bague interne, le centre de courbure des rainures de guidage de la bague externe (1) et le centre de courbure des rainures de guidage de la bague interne (2) sont décalés par rapport au centre du joint à même distance de côtés opposés, ledit joint homocinétique du type fixe étant caractérisé en ce que la position axiale des poches (4a) de la cage (4) est déplacée du centre de courbure de la cage (4) vers le côté externe des rainures de guidage (1a) de la bague externe.
  2. Joint homocinétique du type fixe selon la revendication 1, caractérisé en ce que la quantité de décalage de la position axiale des poches (4a) de la cage est de 1,0 à 3,0 % de la quantité de décalage des rainures de guidage.
  3. Joint homocinétique du type fixe selon la revendication 1 ou 2, caractérisé en ce qu'un mécanisme de précharge (10) est installé entre la bague interne et la cage pour fournir une construction pour combler les interstices des rainures, et en ce qu'un interstice est formé entre la surface sphérique interne de la cage et la surface sphérique externe de la bague interne en état hors charge.
  4. Joint homocinétique du type fixe selon l'une quelconque des revendications 1 à 3, caractérisé en ce que la différence entre la dimension axiale des poches (4a) de la cage et le diamètre des billes de transmission de moment de rotation (3) est comprise entre 1 et 3 µm.
  5. Joint homocinétique du type fixe selon l'une quelconque des revendications 1 à 3, dans lequel la surface du diamètre externe de ladite bague interne (2) est formée avec une section chanfreinée servant de relief qui évite une interférence avec la surface du diamètre interne de la cage (4).
  6. Joint homocinétique du type fixe selon l'une quelconque des revendications 1 à 3, dans lequel la surface du diamètre interne de ladite cage (4) a une surface non sphérique qui empêche les interférences avec la surface de diamètre externe de la bague interne (2).
  7. Joint homocinétique du type fixe selon l'une quelconque des revendications 1 à 6, caractérisé en ce qu'il est utilisé pour un dispositif de conduite d'une automobile.
EP10007894A 2003-10-01 2004-09-27 Joint homocinétique du type fixe Active EP2239478B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2003343173A JP4554181B2 (ja) 2003-10-01 2003-10-01 固定型等速自在継手
JP2004031130A JP4712304B2 (ja) 2004-02-06 2004-02-06 固定式等速自在継手
EP04773567A EP1669622B1 (fr) 2003-10-01 2004-09-27 Joint homocinetique du type fixe

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
EP04773567.5 Division 2004-09-27

Publications (2)

Publication Number Publication Date
EP2239478A1 EP2239478A1 (fr) 2010-10-13
EP2239478B1 true EP2239478B1 (fr) 2011-06-01

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Family Applications (2)

Application Number Title Priority Date Filing Date
EP10007894A Active EP2239478B1 (fr) 2003-10-01 2004-09-27 Joint homocinétique du type fixe
EP04773567A Not-in-force EP1669622B1 (fr) 2003-10-01 2004-09-27 Joint homocinetique du type fixe

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP04773567A Not-in-force EP1669622B1 (fr) 2003-10-01 2004-09-27 Joint homocinetique du type fixe

Country Status (5)

Country Link
US (1) US7704149B2 (fr)
EP (2) EP2239478B1 (fr)
AT (2) ATE511613T1 (fr)
DE (1) DE602004030359D1 (fr)
WO (1) WO2005033538A1 (fr)

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8075411B2 (en) * 2005-09-23 2011-12-13 Gkn Driveline International Gmbh Optimized constant-velocity fixed joint with ball tracks free from undercuts
JP4959177B2 (ja) 2005-11-18 2012-06-20 Ｎｔｎ株式会社 固定式等速自在継手
JP5183930B2 (ja) * 2007-02-02 2013-04-17 Ｎｔｎ株式会社 固定式等速自在継手
JP5143453B2 (ja) 2007-03-20 2013-02-13 Ｎｔｎ株式会社 等速自在継手
DE102009032781A1 (de) 2009-07-10 2011-01-27 Neumayer Tekfor Holding Gmbh Käfig für Kugelgelenk und Kugelgelenk
US8317630B1 (en) * 2011-07-06 2012-11-27 Dana Automotive Systems Group, Llc Plunging type constant velocity joint
JP5840463B2 (ja) 2011-11-10 2016-01-06 Ntn株式会社 固定式等速自在継手
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Also Published As

Publication number Publication date
EP2239478A1 (fr) 2010-10-13
EP1669622B1 (fr) 2010-12-01
US20080096678A1 (en) 2008-04-24
US7704149B2 (en) 2010-04-27
WO2005033538A1 (fr) 2005-04-14
EP1669622A1 (fr) 2006-06-14
ATE511613T1 (de) 2011-06-15
EP1669622A4 (fr) 2008-12-03
ATE490417T1 (de) 2010-12-15
DE602004030359D1 (de) 2011-01-13

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